JPS63176276A - Controller for hydraulic elevator - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Minute Hand] This invention relates to a control device for a hydraulic elevator.

[Conventional technology]

Fig. 2 shows a hydraulic jack for operating a hydraulic elevator similar to that shown as a conventional example in Japanese Patent Application Laid-Open No. 57-126369, 3 a hydraulic pump, 4 an fft motor for driving the hydraulic pump 3, and 5 an oil A tank, 6, is a main circuit for lifting that connects the discharge side of the hydraulic pump 3 and the hydraulic jack 2, and 7 is a main circuit for lifting that branches off from the main circuit for lifting 6 and opens into the oil tank 5, and a part of the main circuit for lifting #I6. The ascending flow rate control valve provided in the constituent bypass circuit 6a, 8 is the back chamber of the ascending flow rate control valve 7, and 9 is the ascending main circuit #! 6 is a rising pilot circuit connected to the back chamber 8 of the rising flow rate control valve 7 and the oil tank 5; 10 is a rising solenoid valve provided in the rising pilot circuit 9; 11, 12;
is the first lifter installed on both sides of the lifter solenoid valve 10 of the lift bike 1-circuit 9. The second variable throttle 13 is a check valve provided on the side of the hydraulic jack 2 from the bypass circuit 6a of the main ascending circuit 6 and the branching portion of the ascending pilot circuit 9. 14 is a descending main circuit connected to the hydraulic jack 2 and opened to the oil tank 5; 15 is a descending flow rate control valve provided in the descending main circuit 14; 17 is a descending main circuit 14 and descending flow rate control valve 15; A lowering pilot circuit is connected to the back chamber 16 and the oil tank 5, 18 is a lowering solenoid valve, 19° and 20 are 3rd and 3rd. The fourth variable aperture is the third variable aperture. The fourth variable throttles 19 and 20 are provided in the lowering pilot circuit 17 along with the lowering solenoid valve 18, so as to be located on both sides of the lowering solenoid valve 18.

Next, the operation of the conventional example configured as above will be explained. When the car 1 is operated to ascend, pressure oil is supplied to the ascending upper &156 by driving the hydraulic pump 3, and initially the entire flow of pressure oil passes through the ascending flow rate control valve 7, and the bypass circuit 6a Return to tank 5. The ascending IA electromagnetic valve 0 is excited, and the pressure oil in the ascending main circuit 6 passes through the first variable throttle 11 of the ascending pilot circuit 9 and flows into the back chamber 8 of the ascending control valve 7, and the ascending control valve 7 is activated. By controlling the valve 7 in the direction in which its passage is closed and reducing the amount of oil returned to the oil tank 5, pressure oil is supplied from the main lifting circuit 6 to the hydraulic jack 2, and the car 1 is lifted and accelerated. Ru. Then, the passage of the ascending flow rate control valve 7 is completely closed, and from this point on, the entire discharge flow rate of pressure oil from the hydraulic pump 3 is supplied to the hydraulic jack 2, and the car 1 moves upward at the maximum speed. Next, when the ascending solenoid valve 10 is demagnetized, the pressure oil in the back chamber 8 of the ascending flow rate control valve 7 passes through the second variable throttle 12 and flows out into the oil tank 5. The control valve 7 is controlled in the direction of opening the passage, and the amount of oil flowing back into the oil tank 5 from the bypass circuit 6a increases, and the amount of oil supplied to the hydraulic jack 2 decreases, causing the car 1 to run at a reduced speed and rise. When the flow rate control valve 7 fully opens its passage, the entire discharge flow rate of pressure oil from the hydraulic pump 3 is returned to the oil tank 5, and the car 1
will be stopped.

In addition, when the car 1 is operated downward, the downward solenoid valve 18
is excited, the pressure oil in the back chamber 16 of the descending flow rate control valve 15 passes through the fourth variable throttle 20 of the descending pilot circuit 17 and flows out into the oil tank 5, and the passage of the descending flow rate control valve 15 opens. , the pressure oil in the hydraulic jack 2 is discharged into the oil tank 5, and the car 1 is lowered and accelerated. Then, the passage of the descending flow rate control valve 15 is fully opened, and from this point on, the car 1 travels downward at the maximum speed. Next, when the descending solenoid valve 18 is demagnetized, pressure oil from the descending main circuit 14 passes through the third variable throttle 19 and flows into the back chamber 16 of the descending flow rate control valve 15 to control the descending flow rate. The valve 15 moves in the direction of closing the passage, the flow rate of the pressure oil passing therethrough is reduced, the car 1 is decelerated, and the descending flow rate control valve 15 completely closes the passage, thereby stopping the car 1.

[Problem that the invention seeks to solve]

Conventional elevator control devices are configured as described above, and can handle changes in load depending on factors such as the number of passengers in the car.
The pressure inside the hydraulic jack fluctuates, and the pressure in the main circuit containing the flow control valve changes accordingly, causing the rise and fall pilots to change.・The flow rate of pressure oil flowing through the circuit also changes. For this reason, the moving speed of the flow rate control valve, that is, the closing speed of the NIrM, varies depending on the pressure inside the jack, causing the car to rise,
The acceleration, deceleration, and slow speed travel (hereinafter referred to as stopping travel) required to roughly match the floor and stop during descending travel vary, resulting in poor ride comfort, reduced interlocking efficiency, and a reduction in the amount of power required. There was a problem with the increase.

This invention was made to solve the above-mentioned problems, and even if the pressure inside the hydraulic jack changes, the car will not be able to accelerate or decelerate when moving up or down.

The object of the present invention is to obtain a control device for a hydraulic elevator that can keep the stopping time constant.

[Means for solving problems]

The hydraulic elevator control device according to the present invention includes a constant difference pressure reducing valve provided between the downstream side of the flow control valve of the main circuit and the oil tank, and the downstream side of the pilot circuit for operating the flow rate control valve of the main circuit. It is connected between the flow rate control valve of the main circuit and the constant difference pressure reducing valve.

[For production]

The hydraulic elevator control device of the present invention is configured as described above, so that the pressure in the main circuit and the pressure at the downstream end of the pilot circuit are always constant regardless of the pressure in the hydraulic jack, and the pressure in the main circuit and the pressure at the downstream end of the pilot circuit are always constant regardless of the pressure in the hydraulic The flow rates of the pressure oil passing through the circuit and the pressure oil flowing out from the flow control valve are also constant, so even if the pressure inside the hydraulic jack changes,
Rise of the basket.

Acceleration, deceleration, and stop travel times during descending travel can be made constant.

〔Example〕

An embodiment of the present invention will be described below with reference to FIG.

In FIG. 1, the same reference numerals as in FIG. 2 indicate the same or corresponding parts, 21 is a constant difference pressure reducing valve, 22 is a first pilot circuit that guides the pressure of the hydraulic jack 2 to the constant difference pressure reducing valve 21, 23
24 is a reflux main circuit in which the constant difference pressure reducing valve 21 is provided, and one end of the reflux main circuit 24 is connected to the ascending main circuit. circuit 6
It is connected to the part where the ascending flow rate control valve 7 downstream side of the bypass circuit 6a, which forms part of the descending main circuit 14, and the descending flow rate control valve 15 downstream side of the descending main circuit 14 are connected, and the other end is opened to the oil tank 5. There is. Further, the downstream ends of the ascending pilot circuit 9 and the descending pilot circuit 17 are connected to the pilot circuit 6a and the descending main circuit 14 immediately before the part where the second pilot circuit 23 is connected to the return main circuit 24, respectively. . Furthermore, the constant difference pressure reducing valve 21 includes a spool valve 21
A piston 21b is provided on one side of the spool valve 21a on which the pressure in the hydraulic jack 2 is applied by the first pilot circuit 22, and a piston 21b is provided on the other side of the spool valve 21a for raising and lowering by the spring force of the spring 21e and the second pilot circuit llI23. A piston 21c is provided on which the pressure on the downstream side of the flow rate control valves 8 and 15, that is, the pressure on the upstream side of the constant difference pressure reducing valve 21 of the recirculation main circuit 24 acts, and when the pressure inside the hydraulic jack 2 is high, the piston 21c acts on the spool valve 21a. An orifice 21 consisting of a V-shaped notch provided
It is configured such that d is reduced. Note that the configuration of this embodiment other than those described above is the same as that shown in FIG. 2.

Next, the operation of this embodiment will be explained. When the car 1 is operated to ascend, pressure oil is supplied to the ascending main circuit 6 by driving the hydraulic pump 3. At this time, the pressure oil that has passed through the rising flow rate control valve 7 is returned to the oil tank 5 through the constant differential pressure reducing valve 21. The pressure inside the hydraulic jack 2 is guided to one side of the constant difference pressure reducing valve 21 by a first pilot circuit 22, and the pressure inside the hydraulic jack 2 is guided to the other side by a second pilot circuit 23. Pressure and spring forces act. As a result, when the pressure inside the hydraulic jack 2 is high, the constant differential pressure reduction: $21 spool valve moves and the orifice contracts, so regardless of the change in the pressure inside the hydraulic jack 2, the pressure inside the hydraulic jack 2 remains constant. The pressure difference in the recirculation main circuit 24 immediately before the constant difference pressure reducing valve 21 becomes constant. Therefore, during the upward operation of the car 1, the pressure of the pressure oil discharged from the hydraulic pump 3, that is, the pressure within the upward lift FR 56, is approximately the same as the pressure within the hydraulic jack 2. In addition, one end of the rising pilot circuit FR1I9 is connected to the main rising circuit 6, and the other end is connected immediately before the constant difference pressure reducing valve 21, so that the pressure difference between both ends of the rising pilot circuit 9 causes the pressure inside the hydraulic jack 2. The flow rate of the pressure oil passing through the lifting pilot circuit 9 remains constant regardless of the current. That is, when the ascending solenoid valve 10 is energized, the flow rate of the pressure oil passing through the ascending pilot circuit 9 and flowing into the back chamber 8 of the ascending flow rate control valve 7 and the ascending solenoid valve 10 are demagnetized. At this time, the flow rate of the hydraulic pressure flowing out from the back chamber 8 of the rising flow rate control valve 7 becomes constant regardless of the pressure inside the hydraulic jack 2.

This means that the opening/closing time of the lift flow control valve 7 is constant, and the acceleration, deceleration, and stop travel times of the car 1 during lift operation are constant regardless of the pressure inside the hydraulic jack 2. , resulting in stable upward driving.

When the car 1 is operated downward, the pressure oil in the hydraulic jack 2 is supplied to the downward flow rate control valve 15. It is discharged into the hydraulic tank 5 through the constant difference pressure reducing valve 21. At this time, the constant difference pressure reducing valve 21
The operation is the same as in the upper W operation described above. and,
Descending pyroso I/times F! 817 has one end connected to the descending upper #j14 and the other end connected just before the constant difference pressure reducing valve 21, so that the pressure difference between both ends of the descending pilot circuit 917 is maintained regardless of the pressure inside the hydraulic jack 2. First, it is always constant, and the flow rate of the pressure oil passing through the descending pilot circuit #517 is constant. In other words, the flow rate of the pressure oil flowing out from the fY chamber 16 of the descending flow rate control valve 15 through the descending pilot circuit 17 when the descending solenoid valve 18 is energized, and the flow rate of the pressure oil flowing out when the descending solenoid valve 18 is demagnetized. The flow rate of the pressure oil flowing into the back chamber 16 of the electromagnetic valve 18 remains constant regardless of the pressure inside the hydraulic jack 2. This means that the opening/closing time of the descending flow rate control valve 15 is constant, and the car 1
During downward operation, the acceleration, deceleration, and stop travel times are constant regardless of the pressure inside the hydraulic jack 2, resulting in stable downward operation.

Note that the present invention is not necessarily limited to the embodiments, and the operation of at least one of the ascending and descending flow control valves may be determined by a pilot circuit; The downstream end of at least one of the pilot) circuits may be connected between the corresponding flow control valve of the main circuit and the tank.

〔Effect of the invention〕

As explained above, according to the present invention, the operation of at least one of the ascending flow rate control valve and the descending flow rate control valve is determined by a pilot circuit, and the pilot circuit of at least one of the above flow rate control valves The downstream end of the is connected to the upstream side of the constant differential pressure reducing valve installed in the main circuit between the corresponding flow rate control valve and the oil tank, so that acceleration, deceleration, and The stopping running time can be kept constant regardless of the pressure saw inside the hydraulic jack, and therefore, stable riding comfort can be ensured regardless of changes in load due to the number of passengers in the cage, etc.
It also has the effect of improving operating efficiency and reducing the amount of power required.

[Brief explanation of the drawing]

FIG. 1 is a hydraulic circuit diagram showing a control device for a hydraulic elevator according to an embodiment of the present invention, and FIG. 2 is a hydraulic circuit diagram showing a conventional control device for a hydraulic elevator. 1. Car, 2. Hydraulic jack, 5. Oil tank,
6・Main circuit for ascending, 6a・Bypass circuit, 7 Flow rate control valve for ascending, 8, 16... Back chamber, 9-・Pilot circuit for ascending, 10, 18 Solenoid valve, 11, 12゜19
．． 20 - Variable aperture, 14 ・Main circuit for lowering, 15...
・Descent flow control valve, 17 ・Descent pilot circuit, 2
1 ・Constant differential pressure reducing valve, 22. 21... 1st ° 2nd pilot circuit, 24 ・Recirculation main circuit. Note that the same reference numerals in the figures indicate the same or corresponding parts. Agent Masuo Oiwa (2 others) Procedural amendment (own party) Showa ＾ September 1st, President of the Japan Patent Office, PA)
1. Indication of the incident Patent Application No. 62-7308 No. 2
, Name of the invention h11-pressure elevator control device 3, Person making the correction Representative: Moriya Shiki 4, Agent address: Mitsubishi Electric Corporation, 2-2-3 Marunouchi, Chiyoda-ku, Tokyo 5, ? IO correct object (1) Drawing 6, contents of amendment (1) Drawing 1 will be corrected as shown in the attached sheet. 7. Attached documents (1) Amended drawings 1 copy Written amendment (voluntary) 20 Name of the invention Hydraulic elevator control device 3. Person making the amendment Relationship to the case Patent applicant address 2-2 Marunouchi, Chiyoda-ku, Tokyo 3 Name (601) Mitsubishi Electric Corporation Representative Moriya Shiki 4, Agent Address 2-2-3-5 Marunouchi, Chiyoda-ku, Tokyo
, Target of correction (1) Drawing 6, Details of correction (1) Drawing 1 will be corrected as shown in the attached sheet. 7. Attached documents

Claims (1)

[Claims] Oil is supplied to the hydraulic jack via an ascending flow rate control valve to cause the car to operate upward, and oil is discharged from the hydraulic jack via a descending flow rate control valve to cause the car to operate downward, and has the above-mentioned flow rate control valve. Between the flow rate valve of the main circuit and the oil tank, there is a spool valve on which the pressure in the hydraulic jack acts on one side and the downstream pressure of the flow rate control valve on the other side. In a hydraulic elevator control system equipped with a constant differential pressure reducing valve whose orifice contracts when the flow rate is high, the downstream end of a pilot circuit provided in at least one flow control valve for operating the flow control valve is connected to the flow control valve of the main circuit. and the constant difference pressure reducing valve.